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US4380356A - Generator rotor, especially turbo-generator rotor with superconducting field winding - Google Patents

Generator rotor, especially turbo-generator rotor with superconducting field winding Download PDF

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Publication number
US4380356A
US4380356A US06/265,650 US26565081A US4380356A US 4380356 A US4380356 A US 4380356A US 26565081 A US26565081 A US 26565081A US 4380356 A US4380356 A US 4380356A
Authority
US
United States
Prior art keywords
sealing
liquid
generator rotor
liquid reservoir
journal
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US06/265,650
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English (en)
Inventor
Erich Weghaupt
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kraftwerk Union AG
Original Assignee
Kraftwerk Union AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kraftwerk Union AG filed Critical Kraftwerk Union AG
Assigned to KRAFTWERK UNION AKTIENGESELLSCHAFT, A GERMAN CORP. reassignment KRAFTWERK UNION AKTIENGESELLSCHAFT, A GERMAN CORP. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: WEGHAUPT, ERICH
Application granted granted Critical
Publication of US4380356A publication Critical patent/US4380356A/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/40—Sealings between relatively-moving surfaces by means of fluid
    • F16J15/43—Sealings between relatively-moving surfaces by means of fluid kept in sealing position by magnetic force
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/12—Casings or enclosures characterised by the shape, form or construction thereof specially adapted for operating in liquid or gas
    • H02K5/124—Sealing of shafts
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K55/00—Dynamo-electric machines having windings operating at cryogenic temperatures
    • H02K55/02—Dynamo-electric machines having windings operating at cryogenic temperatures of the synchronous type
    • H02K55/04—Dynamo-electric machines having windings operating at cryogenic temperatures of the synchronous type with rotating field windings
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E40/00—Technologies for an efficient electrical power generation, transmission or distribution
    • Y02E40/60—Superconducting electric elements or equipment; Power systems integrating superconducting elements or equipment
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S277/00—Seal for a joint or juncture
    • Y10S277/913—Seal for fluid pressure below atmospheric, e.g. vacuum
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S505/00—Superconductor technology: apparatus, material, process
    • Y10S505/825—Apparatus per se, device per se, or process of making or operating same
    • Y10S505/876—Electrical generator or motor structure
    • Y10S505/877—Rotary dynamoelectric type
    • Y10S505/878—Rotary dynamoelectric type with cooling

Definitions

  • the invention relates to a generator rotor, especially a turbogenerator rotor with a superconducting field winding and two concentric rotor parts enclosing a high-vacuum space, wherein on the non-drive side, a hollow shaft end of the outer rotor part is supported in a first bearing and a journal of the inner rotor part, which is brought through the hollow shaft end, is separately supported in a second bearing, and a high-vacuum seal is disposed betwen the hollow shaft end and the journal.
  • a similar generator rotor is already known from Swiss Pat. No. 552,907.
  • the hollow shaft end of the outer rotor part and the journal of the inner rotor part are not supported separately, but rather in a common bearing.
  • sealing bellows are provided in the known generator rotor. The bellows are arranged between the inner circumference of the hollow shaft end and the outer circumference of the journal.
  • the high-vacuum seal must be able to take up high-frequency radial vibrations between the hollow shaft end and the journal, having an amplitude of, for instance 10 to 20 ⁇ M in normal operation; this amplitude can increase for short periods when resonance positions are traversed.
  • the high-vacuum seal must additionally be able to take up high-frequency radial stresses which can result from changes in the bearing alignment in the horizontal and/or vertical direction, with corresponding eccentric positions of the hollow shaft end and the journal.
  • the high-vacuum seal must be constructed in such a way that it can take up the relatively high centrifugal stresses.
  • the high-vacuum seal is expected to have a long service life and good maintainability, i.e. it must ensure an uninterrupted operating time of the generator of at least 20,000 to 25,000 hours and, if so indicated by inspection, it must be exchangeable with little installation effort.
  • sealing elements cannot meet these requirements for a high-vacuum seal.
  • sealing elements such as metal bellows, diaphragm discs and the like are destroyed within a very short time, i.e. they only reach a fraction of the specified operating times.
  • a generator rotor especially a turbo-generator rotor with a superconducting field winding, comprising an inner and an outer concentric rotor part having a non-drive side and enclosing a high-vacuum space, a first and a second bearing disposed on the non-drive side, a hollow shaft end of the outer rotor part being supported in the first bearing, a journal of the inner rotor part being extended through the hollow shaft end and separately supported in the second bearing, a high-vacuum contactless liquid seal disposed between the hollow shaft end and the journal and having a sealing gap formed therebetween, a co-rotating sealing-liquid reservoir connected to the liquid seal, and magnetic field means for holding magnetic sealing liquid in the sealing gap.
  • the magnetic sealing liquid held in the sealing gap by the magnetic field ensures reliable sealing of the high-vacuum space against the ambient atmosphere, and small losses of the sealing-liquid due to evaporation are compensated from the sealing liquid reservior. Due to the fact that the high-vacuum seal is constructed as a contactless liquid seal, the high static and dynamic stresses have no effect on the operational reliability of the seal.
  • the sealing-liquid reservoir is at least partially disposed radially inward of the sealing gap, i.e. it is at a smaller diameter than the sealing gap, at least at certain regions.
  • the sealing-liquid reservoir has a radially inner boundary being disposed at a radial distance from the sealing gap for adjusting input pressure of sealing-liquid in the sealing gap between predetermined limits in operation, i.e. it is done so that the input pressure of the sealing liquid in the sealing gap does not exceed or fall below predetermined limits in operation.
  • the limits of the input pressure can then be determined in such a way that, on one hand the requirement of replenishing is met, and on the other hand the safety margin against a seal break-through into the high-vacuum space is not diminished, or only inappreciably so.
  • the sealing-liquid reservoir which is disposed inward of the gap, has a volume sufficient for compensating all sealing-liquid losses within a predetermined implantation interval.
  • the liquid seal has adjoining axially and radially directed canals formed therein connecting the sealing-liquid reservoir to the sealing gap.
  • the connection between the sealing gap and the sealing-liquid reservoir can be provided in a centrifugal-force-proof way and with little structural expense.
  • radially directed partitions subdividing the sealing-liquid reservoir into a plurality of chambers.
  • the partitions act in this embodiment as carriers for the sealing liquid and thereby prevent slippage between the sealing liquid and the wall of the sealing liquid reservoir.
  • At least one filling canal leading from outside the rotor to the sealing-liquid reservoir leading from outside the rotor to the sealing-liquid reservoir, the filling canal being accessible and closeable from outside the rotor.
  • FIG. 1 is a fragmentary, diagrammatic longitudinal-sectional view of a turbo-generator rotor having two concentric rotor parts, in the vicinity of the bearing on the non-drive side;
  • FIG. 2 is a detailed fragmentary view of the high-vacuum seal according to FIG. 1 in the vicinity of the bearings;
  • FIG. 3 is a fragmentary cross-sectional view of the high-vacuum seal taken along the line III--III in FIG. 2, in the direction of the arrows.
  • FIG. 1 a turbo-generator rotor with a superconducting field winding and two concentric rotor parts which enclose a high-vacuum space are supported on the non-drive side.
  • the support is furnished by means of a hollow shaft end 1 of the outer rotor part in a first bearing 2, and by means of a journal 3 of the inner rotor part brought through the hollow shaft end 1 and supported in a second bearing 4.
  • the two separate bearings 2, 4 in the embodiment example shown are disposed in a common bearing block 5 and are accessible from the outside after the upper part 60 of a multipart bearing housing 6 is removed.
  • annular space 7 which is directly connected to the high-vacuum space of the turbo-generator rotor and is sealed-off from the ambient atmosphere by a high-vacuum seal, designated as a whole with reference numeral 8.
  • a high-vacuum seal designated as a whole with reference numeral 8.
  • further sealing rings 9 are additionally disposed between the hollow shaft end 1 and the journal 3. These sealing rings therefore merely serve as a rough seal, i.e. they are not suited for taking over the purpose of the high-vacuum seal 8.
  • FIGS. 2 and 3 For a further explanation of the construction and operation of the high-vacuum seal 8, reference is made to FIGS. 2 and 3.
  • a cut 10 is provided at the free end of the hollow shaft end 1, the sealing housing 81 being inserted with a play-free fit into this cut 10 and being held by means of several axial screws 810, which are distributed over the circumference thereof.
  • the seal housing 81 is provided with a cut 811.
  • the sealing module 82 is secured in the axial direction by the shoulder 830 of a head cover 83 projecting into the recess 811.
  • the head cover 83 is fastened to the seal housing 81 by means of several screws 831 distributed over the circumference thereof.
  • a sealing ring 812 is provided between the end faces of the cut 811 facing each other and the sealing module 82, a sealing ring 832 is provided between the end faces of the shoulder 830 facing each other and the sealing module 82, and a sealing ring 833 is disposed between the contact surfaces of the head cover 83 and the seal housing 81.
  • the head cover 83 has the further purpose of receiving a sealing-liquid reservoir 834.
  • This sealing-liquid reservoir 834 which surrounds a smaller diameter step 30 of the journal 3 in ring-fashion, is machined as a concentric recess into the head cover 83 and is sealed liquid-tight by means of a welded-in face plate 835.
  • the sealing liquid reservoir 834 is connected to the sealing module 82 by several radially-directed canals 836 which are formed in the head cover 83 and which are followed by axial-directed canals 813 that are cut as slots into the inner periphery of the housing 81 at the circular cut 811.
  • a filling canal 837 which is accessible from the outside and can be closed off in a liquid-tight manner by means of a threaded plug 838, also leads into the sealing liquid reservoir.
  • the sealing module 82 includes pole pieces 820 and 821, which surrounds the journal 3 in ring-fashion and are provided at their inside circumference or periphery with sealing combs 8200 and 8210, respectively. These sealing combs 8200 and 8210 form a sealing gap designated with reference character S toward the journal 3. The gap is dimensioned in such a way that no metallic contact occurs. Between the two pole pieces 820 and 821 there are disposed disc-shaped permanent magnets 822, which are uniformly distributed over the circumference and are also aligned in the same manner with respect to their polarity. The connection between the axial canals 813 and the sealing gap S is accomplished through radially-directed canals 823 and 824 which are cut into the pole pieces 820 and 821 and lead together into the sealing gap S between the two pole pieces 820 and 821.
  • the sealing-liquid reservoir 834 is filled up through the filling canal 837 with a magnetic sealing liquid.
  • magnetic sealing liquids are colloidal suspensions of magnetic particles in a carrier liquid.
  • liquids with a low vapor pressure such as with a diester base, are especially suitable as the carrier liquid. Due to the radial distance between the inner boundary of the sealing liquid reservoir 834 and the inner circumference of the sealing combs 8200 and 8210, which is designated with reference character A, the magnetic sealing liquid is automatically pumped into the sealing gap S by the action of centrifugal force.
  • the magnetic sealing liquid is then held in the sealing gap S, so that the annular space 7, which is in communication with the high-vacuum space, is reliably sealed from the ambient atmosphere. Since no friction losses occur due to rotation in the sealing gap S, the losses of sealing liquid are extremely small. The sealing liquid losses caused by evaporation and by wetting the journal 3 in the case of axial motion, are compensated by replenishment from the radially lower-situated sealing liquid reservoir 834.
  • the already-mentioned radial distance A is chosen in such a way that on one hand the requirement of replenishing the sealing liquid is met, and on the other hand, the safety margin against a seal-breakthrough into the high-vacuum space is not appreciably reduced.
  • the volume determined by the radial distance A and the axial width B of the sealing liquid reservoir 834 and the diameter of the step 30 of the journal 3, is chosen in such a way that all sealing liquid losses can be compensated within a given inspection interval.
  • the axial distance between the step 30 of the journal 3 and end face plate 835 of the sealing liquid reservoir 834 designated with reference character Z must be made larger than the axial displacement due to thermal dilatation.

Landscapes

  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Superconductive Dynamoelectric Machines (AREA)
  • Windings For Motors And Generators (AREA)
US06/265,650 1980-05-23 1981-05-20 Generator rotor, especially turbo-generator rotor with superconducting field winding Expired - Fee Related US4380356A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3019864A DE3019864C2 (de) 1980-05-23 1980-05-23 Generatorläufer, insbesondere Turbogeneratorläufer, mit supraleitender Erregerwicklung
DE3019864 1980-05-23

Publications (1)

Publication Number Publication Date
US4380356A true US4380356A (en) 1983-04-19

Family

ID=6103204

Family Applications (1)

Application Number Title Priority Date Filing Date
US06/265,650 Expired - Fee Related US4380356A (en) 1980-05-23 1981-05-20 Generator rotor, especially turbo-generator rotor with superconducting field winding

Country Status (4)

Country Link
US (1) US4380356A (de)
EP (1) EP0040733A3 (de)
JP (1) JPS5716573A (de)
DE (1) DE3019864C2 (de)

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4478424A (en) * 1984-01-27 1984-10-23 Ferrofluidics Corporation Ferrofluid seal apparatus and method
US4545587A (en) * 1984-11-20 1985-10-08 Ferrofluidics Corporation Coaxial, multiple-shaft ferrofluid seal apparatus
US4577340A (en) * 1983-09-19 1986-03-18 Technicare Corporation High vacuum rotating anode X-ray tube
EP0367375A1 (de) * 1988-11-04 1990-05-09 Ferrofluidics Corporation Langlebige mehrstufige Ferrofluid-Dichtung mit Ferrofluid-Behälter
US4995622A (en) * 1989-02-07 1991-02-26 Nippon Pillar Packing Co., Ltd. Magnetic fluid seal device
US5047392A (en) * 1989-03-21 1991-09-10 Troy Investments Inc. Diamagnetic colloids based seals
US5474302A (en) * 1992-08-27 1995-12-12 Ferrofluidics Corporation On-site fillable ferrofluidic seal
US5593164A (en) * 1992-10-08 1997-01-14 Ferrofluidics Corporation Ferrofluidic seal centering ring
US5806856A (en) * 1992-08-27 1998-09-15 Ferrofluidics Corporation On-site fillable liquid magnetic seal
CN1316160C (zh) * 2004-11-16 2007-05-16 吴雳鸣 双磁极双随动动静间隙处密封装置
US20100230903A1 (en) * 2008-07-07 2010-09-16 Eagle Industry Co., Ltd. Sealing apparatus
US20110182756A1 (en) * 2007-08-17 2011-07-28 Sulzer Pumpen Ag Multi-Phase Pump
US20110198814A1 (en) * 2009-09-24 2011-08-18 Kotaro Oshita Seal device
US20110215533A1 (en) * 2010-03-08 2011-09-08 Beijing Jiaotong University Reciprocating shaft's sealing apparatus combined a ferrofluid seal with a c-slip-ring and a yx-seal-ring
US20120018958A1 (en) * 2010-07-23 2012-01-26 Chi-Yun Kung Magnetic Fluid Shaft-Sealing Device
CN102345626A (zh) * 2010-07-28 2012-02-08 龚祺允 磁流体密封装置
CN102537367A (zh) * 2012-01-12 2012-07-04 北京理工大学 一种磁流体轴密封装置
CN103104706A (zh) * 2013-01-16 2013-05-15 南通密炼捏合机械有限公司 干燥机轴头密封装置
US11674600B2 (en) * 2018-05-30 2023-06-13 Siemens Energy Global Gmbh & Co., Kg Assembly, more particularly turbomachine, comprising a shaft seal device

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3407275A1 (de) * 1984-02-28 1985-08-29 Kraftwerk Union AG, 4330 Mülheim Einrichtung an einer rotierenden maschine zur waermebeweglichen und abdichtenden kopplung zweier konzentrischer wellen
JPS6126425A (ja) * 1984-07-13 1986-02-05 株式会社明電舎 変圧器の保護装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3834775A (en) * 1972-05-26 1974-09-10 Litton Systems Inc Ferrohydrodynamic low-friction bearing with improved volume compensation and fluid seal
SU653470A1 (ru) * 1977-12-02 1979-03-25 Ивановский энергетический институт им.В.И.Ленина Магнитожидкостное уплотнение
US4304411A (en) * 1980-04-17 1981-12-08 Mechanical Technology Incorporated Magnetic/centrifugal-fluid seal
US4323801A (en) * 1979-05-09 1982-04-06 Kraftwerk Union Aktiengesellschaft Bearing system for a rotor of electric machines, especially for a rotor of a turbogenerator with a superconductive field winding

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD12642U (de) *
DE929648C (de) * 1952-11-07 1955-08-01 Licentia Gmbh Axiale OEldichtung
DE1956759C3 (de) * 1969-11-12 1974-06-12 Dornier System Gmbh, 7990 Friedrichshafen Spaltdichtung zwischen einer Fläche und einem relativ zu dieser Fläche beweglichen und mit der Fläche einen abgeschlossenen Innenraum bildenden Körper mit einer der Fläche gegenüberliegenden Dichtleiste
CH552907A (de) * 1972-12-07 1974-08-15 Bbc Brown Boveri & Cie Lageranordnung des rotors einer elektrischen maschine.
DE2628831A1 (de) * 1976-06-26 1978-01-05 Maschf Augsburg Nuernberg Ag Dichtung
DE2841163C2 (de) * 1978-09-21 1985-09-12 Siemens AG, 1000 Berlin und 8000 München Elektrische Maschine mit einem Läufer mit supraleitender Erregerwicklung

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3834775A (en) * 1972-05-26 1974-09-10 Litton Systems Inc Ferrohydrodynamic low-friction bearing with improved volume compensation and fluid seal
SU653470A1 (ru) * 1977-12-02 1979-03-25 Ивановский энергетический институт им.В.И.Ленина Магнитожидкостное уплотнение
US4323801A (en) * 1979-05-09 1982-04-06 Kraftwerk Union Aktiengesellschaft Bearing system for a rotor of electric machines, especially for a rotor of a turbogenerator with a superconductive field winding
US4304411A (en) * 1980-04-17 1981-12-08 Mechanical Technology Incorporated Magnetic/centrifugal-fluid seal

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4577340A (en) * 1983-09-19 1986-03-18 Technicare Corporation High vacuum rotating anode X-ray tube
US4478424A (en) * 1984-01-27 1984-10-23 Ferrofluidics Corporation Ferrofluid seal apparatus and method
US4545587A (en) * 1984-11-20 1985-10-08 Ferrofluidics Corporation Coaxial, multiple-shaft ferrofluid seal apparatus
EP0367375A1 (de) * 1988-11-04 1990-05-09 Ferrofluidics Corporation Langlebige mehrstufige Ferrofluid-Dichtung mit Ferrofluid-Behälter
US4995622A (en) * 1989-02-07 1991-02-26 Nippon Pillar Packing Co., Ltd. Magnetic fluid seal device
US5047392A (en) * 1989-03-21 1991-09-10 Troy Investments Inc. Diamagnetic colloids based seals
US5474302A (en) * 1992-08-27 1995-12-12 Ferrofluidics Corporation On-site fillable ferrofluidic seal
US5806856A (en) * 1992-08-27 1998-09-15 Ferrofluidics Corporation On-site fillable liquid magnetic seal
US5593164A (en) * 1992-10-08 1997-01-14 Ferrofluidics Corporation Ferrofluidic seal centering ring
CN1316160C (zh) * 2004-11-16 2007-05-16 吴雳鸣 双磁极双随动动静间隙处密封装置
US20110182756A1 (en) * 2007-08-17 2011-07-28 Sulzer Pumpen Ag Multi-Phase Pump
US20100230903A1 (en) * 2008-07-07 2010-09-16 Eagle Industry Co., Ltd. Sealing apparatus
US20110198814A1 (en) * 2009-09-24 2011-08-18 Kotaro Oshita Seal device
US8328199B2 (en) * 2009-09-24 2012-12-11 Eagle Industry Co., Ltd. Seal device
US20110215533A1 (en) * 2010-03-08 2011-09-08 Beijing Jiaotong University Reciprocating shaft's sealing apparatus combined a ferrofluid seal with a c-slip-ring and a yx-seal-ring
US20120018958A1 (en) * 2010-07-23 2012-01-26 Chi-Yun Kung Magnetic Fluid Shaft-Sealing Device
US8419019B2 (en) * 2010-07-23 2013-04-16 Chi-Yun Kung Magnetic fluid shaft-sealing device
CN102345626A (zh) * 2010-07-28 2012-02-08 龚祺允 磁流体密封装置
CN102345626B (zh) * 2010-07-28 2013-10-09 龚祺允 磁流体密封装置
CN102537367A (zh) * 2012-01-12 2012-07-04 北京理工大学 一种磁流体轴密封装置
CN102537367B (zh) * 2012-01-12 2014-12-03 北京理工大学 一种磁流体轴密封装置
CN103104706A (zh) * 2013-01-16 2013-05-15 南通密炼捏合机械有限公司 干燥机轴头密封装置
CN103104706B (zh) * 2013-01-16 2015-07-29 南通密炼捏合机械有限公司 干燥机轴头密封装置
US11674600B2 (en) * 2018-05-30 2023-06-13 Siemens Energy Global Gmbh & Co., Kg Assembly, more particularly turbomachine, comprising a shaft seal device

Also Published As

Publication number Publication date
DE3019864C2 (de) 1982-05-27
JPS5716573A (en) 1982-01-28
DE3019864A1 (de) 1981-12-03
EP0040733A2 (de) 1981-12-02
EP0040733A3 (de) 1982-06-30

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AS Assignment

Owner name: KRAFTWERK UNION AKTIENGESELLSCHAFT, MULHEIM (RUHR)

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:WEGHAUPT, ERICH;REEL/FRAME:004043/0698

Effective date: 19810512

Owner name: KRAFTWERK UNION AKTIENGESELLSCHAFT, A GERMAN CORP.

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